Hydraulic control valve



June E2, 1951 M. E. cUsHMAN 2,556,719

HYDRAULIC CONTROL VALVE Filed April 25, 1947 FIGA INVENTOR.

MAURICE E CusHMAN ATTORNEY Patented June 12, 1951 UNITED HYDRAULIC CONTROL VALVE Maurice E. Cushman, Verona, N. J., assgnor to Curtiss-Wright Corporation, a corporation of Delaware Application April 25, 1947, Serial No. 743,748

Claims.

This invention relates to hydraulic control systems and to valves therefor and is concerned particularly with a hydraulic control Valve operable to connect and disconnect a pressure source relative to a hydraulic circuit. Y

Certain hydraulic systems include a normal pressure source which may at times provide insufcient pressure for system operation, and an auxiliary pressure source, such as an accumulator, which can be co-nnected into the system when the normal pressure source is inadequate. It is an object of this invention to provide a valve for connecting and disconnecting an auxiliary pressure source relative to a hydraulic system, an additional object being to provide such a valve which will operate in response to preselection of valve position and in response to pressure conditions in the hydraulic system. A further object of the invention is to provide a delayed action hydraulic valve, the delay depending on pressure conditions in the hydraulic system. A further object is to provide a hydraulic system and a valve therefor applicable to hydraulically controlled and operated aircraft propellers and other aircraft instrumentalities, wherein operating pressure shutoff may be desired in a hydraulic system at times when certain positional relationships of the system components exist, such relationships at times following a change in the position of the components relative to one another.

This application comprises improvements, in part, in the hydraulically controllable pitch propeller system disclosed in my copending patent application Serial No. 651,264 filed March 1, 1946, and entitled Hydraulic Pitch Changing System. The present invention, however, may be applied not only to the propeller pitch changing system of said application but `to other forms of hydraulic systems and its use isnot limited to any particular system. While the system and valve of the invention are designated as hydraulic in character, they may be adapted for pneumatic operation and where the term hydraulic is used it is to be read as including pneumaticf The objects of the invention above outlined, and others which will become apparent as the description proceeds, are achieved by the structure and arrangements set forth in the following detailed description when read with the accompanying drawing. It is to be expressly understood that the drawing is employed for illustration of only a single possible embodiment and is not to be construed as limiting the scope of the invention, reference being had to the appended claims for this purpose.

In the drawing, in which similar reference characters designate similar parts, Fig. 1 is a schematic diagram of a hydraulic system incorporating the features of the invention, and

Figs. 2, 3 and 4 are enlarged longitudinal sections of a contro-l valve as incorporated in Fig. 1, showing the valve components in different positions of adjustment.

Referring rst to Fig. 1, I0 represents a piston type hydraulic motor which as shown is incorporated in a controllable pitch propeller. A piston l2, of annular form, embraces, rotates with, and is axially movable along a propeller shaft I3,the piston being movable in a stationary cylinder I4 having conduits I6 and I8 communicating with opposite ends thereof. The shaft I3 carries a propeller hub 2E Within which are journalled one or more propeller blades 22 the latter being alterable in pitch during propeller operation by means of racks 24, engaging gear teeth onthe propeller blades, the racks being directly connected to the piston l2 and passing through the rear wall of the hub 20. The hub is rotatable, and is sealed with respect to the cylinder I4 through sealing means 2li.

The conduits I6 and I8 lead to ports in a housing 28 said housing containing a valve 30. The housing 28 likewise has a pressure nuid supply port 32 connected to the output of a pump 38 through a pipe 40, this pipe also having a branch leading to a port 44 in a control valve 42. Ports 34 and 36 at the ends of the housing 28 are connected with a conduit 46 leading to a sump or reservoir 48.

During normal operation of the system as thus far described, the valve 30 is controlled by a governing device such as 50, and may move upwardly or downwardly to admit pressure fluid from the port 32 to the conduits I6 or I8, respectively to Vdecrease or increase the pitch of the propeller blade 22. While pressure fluid is admitted to either end of the `cylinder I4, the opposite end of the cylinder is opened to the sump ports 34 or 36 by the valve 38. Normal operation of the valve 30 by the governor 5I! causesl blade pitch change to maintain the propeller at constant rctationalspeed. Forced movement of the valve 30 may be imposed, as will be described, to cause blade pitch changes beyond the control of the governor.

The intake of the pump 38 is connected to the sump conduit 46 by a conduit 52. A port 54 on the control valve 42 is likewise connected to the sump conduit 46. The conduit I6 leading to the front or decrease pitch end of the cylinder I4 is connected to a port 58 on the control valve 42 by a conduit 60. A pressure fluid accumulator E52 is connected through a conduit 6d to a port t5 on the control valve 132.

The control valve 42 as will be described in detail later serves at times to connect the accumulator 62 with the pump output line dil.

The propeller I of Fig. 1 is capable of being feathered in operation, such feathering being desirable to reduce the drag of a propeller when it is not operating or being driven by a power plant. The need for propeller feathering mechanism is well known in the art. A control is provided to feather the propeller, in the form of a manually operable lever S8 which carries a projection l which, when the lever S3 is moved tov the left, tothe feather position, engages an abutment i2 on the stem of the valve Sli, forcing downward movement oi the valve regardless oi signals imparted to the Avalve by the governor 59, the valve thereby opening the pressure line 48 to the rear or pitch increasing end of the cylinder i4. Pressure provided by the pump 33 will thereby increase propeller pitch toward a eathering position. However, since the fluid pump 3S is normally driven by the propeller or by the shaft I3, pump nuid delivery varies with propeller rotational speed. If the propeller is windmilling, its speed is controlled by air speed and blade pitch, and as a high pitch position is reached, short of the feathering position, where the shaft I3 is turning slowly, the pump 33 will generate insuiicient pressure to accomplish final propeller feathering. To provide the high pressure necessary to accomplish propeller final feathering in a short time interval, the accumulator @2 is connected to the system pressure line i5 through the normally open valve i2 and the conduit fill. The accumulator, comprising a reservoir of pressurized uid, will provide suicient additional fluid in addition to that iurnished by the pump S, to place the propeller in full feathered position.

When the lever 68 is moved leltwardly to feather the propeller, a projection ill on the lever relaxes pressure on a valve stem 'it of the valve 42 for a purpose which will become clear as the specification proceeds. This relaxation of pressure on the valve stem 'i5 serves ultimately to allow shutoff of the accumulator from the line 44 by closing of the valve 42 when feathering is finally accomplished.

When it is desired to unfeather the propeller, the lever 68 is moved rightwardly to the normal position, relaxing pressure on the valve stem l and restoring the valve 3! to control by the governor G. Concurrently, pressure is imposed on the valve stem 'I6 serving to open the valve 42 to allow accumulator fluid to pass to the system pressure line 453 and thence to the valve housing 28. The valve 3l) in the latter, having been restored to governor control, will call for pitch reduction-that is, the pressure line 4:3 and its port 32 will be placed in communication with the decrease pitch pressure line i6, passing hydraulic fluid from the accumulator 62 to the front or decrease pitch end of the propeller cylinder Ed thereby enforcing pitch reduction. As pitch is reduced, the propeller will begin to windmill, picking up rotational speed whereby the pump 38 is driven and again delivers pressure fluid for governed propeller operation. As the iluid pressure from the pump 33 builds up, the accumulator 62 will be recharged through the open valve so that the accumulator will be available for future eathering operations when needed.

The detailed operation of the control valve 42 will now be described along with the relationships of the pressures existing in the system, in the accumulator 62, and in the pressure line d and in the pitch decrease line l, under the several operating conditions encountered during normal and unfeathering operation (Fig. 2), initial feathering operation (Fig. 3), and final feathering operation (Fig. 4).

The valve i2 in Figs. 2, 3 and 4 comprises a two-piece housing including a base element 83 and hollow element 82 tted thereto. The element contains an axial hole through which the' valve stem *IS enters the valve assembly, the stem being sealed in the element 8e3 by an O ring 84 retained by a cover plate $5. An axial bore within the element 3Q is slidably engaged by a sleeve 83 sealed relative to the element 88 by an O ring Si), said sleeve having a bore somewhat larger than the stem l@ through which said stem passes. The sleeve 88 is integral with a cup 92 press iitted in a bore in an axially mov'- able valve member 94, the cup Q2 being secured to the member Sil as by peening at the point 96. The cup 92 contains a flexible beilows sii closed at its leftward end by a partition let and secured or sweated at its rightward end to the bottom of the cup 92. The interior of the bellows B communicates through the annular passage around the valve stem l with the port 5B formed in the element 88, this port as previously described, being connected to the front or leftward end of the cylinder ill as shown in Fig. l. When moved by the feather lever 58 (Fig. l) the stem 'i6 either relaxes contact with the bellows closure Ill, as shown in Figs. 3 and 4, or forces the bellows closure leitwardly as shown in Fig. 2. The bellows closure carries a pin m2 passing through an orice IBI; in a cover ISE within the member 84, said cover serving to close a ball valve chamber H38 formed within the member. An orice I It), coaxial with the orifice IM, establishes communication between the chamber Iil and the outside of the member 94 near the left end thereof through a cross drilling H2. The chamber |08 contains a ball III which is movable to close ofi either the orifice IIB or the orice |04 for a purpose to be described.

The member 94 is stepped in diameter, its rightward end having the largest diameter and having O ring sealed fitting engagement with the wall of a large bore. A chamber I I6 is defined in the housing element E52 leftwardly of the large diameter part of the member ed, the chamber I I6 registering with the sump port 54. The rightward end of the bore I i5 is terminated by the leftward wall of the housing element 8B and forms with the rightward end of the member 94 a chamber H8 which communicates at all times with the chamber Hi8 through a drilling |20 in the member 945. The chamber IIE communicates at all times with the cavity in the member Q11 in which the bellows 98 is disposed, through a drilling |22.

The housing element 82 is provided with an intermediate diameter bore defining a chamber |24 to which an intermediate diameter portion IZS of the member all is O ring sealed and tted. The leftward end of the member 94,1eftwardly of the drilling I l2 and the orifice il@ is provided with a small diameter portion comprising a valve face i225 engageable with a valve seat ISU in the left ward end of the housing element 82. The left side of the valve seat I3@ communicates with the port 4d leading to the pump outlet, while the right side of the seat I3, comprising the chamber |24,

communicates at all times with the port 66 leading to the accumulator 62. Also, the drilling II2 and the orice I I are continuously in communication with the port 66. v

Under normal operating conditions and for unfeathering, the valve elements occupy the positions shown in Fig. 2, wherein the valve stem 76, through the bellows pin |02, forces the ball valvek I I4 to close the orice I I0. This places the large diameter chamber I I8 in communication with the sump port 54 through the passage |20, the chamber |08, the orice |04 and the passage |22, so that there is no force, save that exerted by the iiuid pressure in the port 58 acting on the interior of the bellows 98 and on the end of the sleeve 88 and that exerted by the stem 10, to cause leftward movement of the main valve member 94. Since accumulator pressure exists at the ports 69 and 44, this pressure is imposed on the entire leftward face of the valve member 94, over the area defined by the intermediate diameter bore of the chamber |24, thus forcing or holding the valve member 94 to the right with the valve face |20 off of the seat |30.

This communication of the ports 44 and 66 with one another continues throughout normal operation of the propeller or hydraulic system.

It should be noted here that such pressure as may exist in the pitch decreasing end of the lpropeller operating cylinder is freely communicated to the port 58 of the valve 42, this pressure acting within the bellows 98 to enforce movement of the pin |02 leftwardly to hold the ball I I4 in a closing position against the orifice I I0. Since the-bellows diameter is substantially less than the diameter of various portions of the member 94 subject to other pressures, the pressure within the bellows, by itself, will have no effect in causing movement of the member 94.

Now referring to Fig. 3, the position of the valve elements is shown when propeller feathering is initiated by relaxing pressure on the valve stem 16, due to movement of the feather handle 68 to the feather position. In this phase of operation, the only change in the position of the valve elements is the relaxation of `pressure on the stem '16. Otherwise, the valve member 94 remains in the same position as in Fig. 2, retaining communication between the valve ports 44 and 06. At this time, propeller pitch change will be urged in a pitch increasing direction, beyond the control of the governor 50, and moderate pressure will remain in the forward end of the propeller cylinder I4 which is communicated through the conduits I6 and 60 to the port 58 and to the interior of the bellows 99. Expansion of the bellows from this internal pressure holds the ball valve II4 against the orifice I I0. This pressure at the port ES is sufficient to hold the ball valve against the orice I I 0 despite the higher pressure existing in the chamber |24.

ns propeller pitch approaches a feathering angle, propeller rotational speed will decrease and concurrently, output from the pump 38 willA decrease. However, pressure fluid from the accumulator 62 will continue to enforce blade pitch change until the final position of feathering of the propeller is reached. This final position of feathering is limited by leftward movement of the propeller piston I2 in its cylinder I4. When the piston I2 reaches its limit of movement, fluid pressure in the left end of the cylinder I4 and in the line I6 will decrease to sump pressure. Since the leftward end of the cylinder I4 is in continual communication with the'interior of the 6I bellows 98, when the pressure lfalls off, the bellows 98 will retract as shownin Fig. 4 due to its own spring force, moving the pin |02 out of contact with the ball ||4 and allowing the ball to move from the orifice`||0 to close the orifice |04.

Opening of the orifice ||0 transmits accumulator iiuid pressure from the port 66 through the chamber |08, the passage |20 and into the large diameterV chamber II8 at the rightward end of the member 04. While the unit pressure in the chamber I I8 and in the chamber |24 is the same, the effective area of the chamber Il8 is considerably greater than that of the chamber |24 and thus, the valve member 94 is forced to move leftwardly whereby the valve face |23 on the member 94 engages the valve seat |30 on the element 82. This closes the ports 44 and 66 from communication with one another and seals off the accumulator from the balance of the hydraulic system. After Vclosure of the valve |28 against the seat |30, any leakage or pressure reduction in any part of the system communicating with the port 44 becomes immaterial since the system is out of operation, the propeller is stationary and in feathering pitch and no further need for pressure in the system currently exists.

By the above valve action sequence it `will be clear that the stem 'I6 is utilized to preselect closure of the valve face |28 against the seat |30 to shut off accumulator pressure from the system; but such valve closure is not attained until final feathering position is reached and until pressure in that part of the' circuit communicating with the port 50 has fallen to a negligible value. In'eifect, the valve has delay action, the delay, after pre-selection, hinging upon the completion of feathering or upon the completion of a complete stroke of the hydraulic motor.

Should re-starting of the engine and restoration of the propeller system to normal operating pitch be desired, the lever 68 is returned to the normal position which drives the valve stem It inwardly to enforce movement of the ball I i4 to close the orifice H0. As previously described in connection with Fig. 1, the chamber IIB is thus bled to the sump and accumulator pressure acting inthe chamber 24 on the annular area between the valve seat |30 and the intermediate bore enforces opening of the valve member 94, to establish communication between the ports 44 and B6.

From the foregoing detailed description it will be seen that the valve unit 42 is in effect a hydraulic servo mechanism operated by relatively large pressure which is valved to appropriate cavities within the main valve assembly by small operating forces. The details of valve construction are susceptable to numerous changes and modifications; for instance, the bellows unit 98 may be replaced by a piston unit utilizing springs for urging the ball valve operating pin |022 against the pressure existing in the port 59. Numerous mechanical modifications and rearrangements of the elements may be embodied in the valve without altering its essential mode of operation.

It is contemplated that a valve such as 42 might be utilized to good advantage for relieving operating pressure from a hydraulic system when a hydraulic motor such as the motor on the propeller in Fig. 1 has reached a terminal position. Hydraulic systems of the sort used in machine tools, in hydraulic remote control devices, in aircraft ap and landing gear operators and many assegna 7 others, are susceptible to the incorporationof the teachings of this invention.

Though but a single embodiment illustrating the invention has been illustrated and described, it is to be understood that the invention may be applied in various forms. Changes may be made in the arrangements shown without departing from the spirit -or scope of the invention as will be apparent to those skilled in the art and reference should be made to the appended claims for a definition of the limits of the invention.

What is claimed is:

1. In a hydraulic servo shutoff valve between pressure lines having variable pressure phases, a housing having coaxial different diameter bores defining cavities and a coaxial valve seat of diameter smaller than said bores; a valve member slidable in said bores having a seat engaging portion, a smaller bore engaging portion and a larger bore engaging portion, said member having a chamber therein including valve seats and passages connecting said chamber with said cavities, a servo valve within said valve member movable to a rst position against one of said seats to establish communication `between said smaller bore cavity and said larger bore cavity and alternatively movable to a second position against another of said seats to establish communication between said larger bore cavity and a pressure reliei` connection, and means to move said servo Valve to said first position.

2. A hydraulic system comprising a conduit at system pressure, a conduit from an accumulator, a shutoi valve between said system and accumulator conduits actuatable by accumulator and system pressure, a valve position selector movable to valve opening and closing positions, and a servo device in said valve responsive to pressure of an element of the system to apply system pressure on the valve to hold said valve open, said device becoming inoperative in response to substantial decrease of pressure in said element of the system subsequent to moving of said selector to a valve closing position and applying accumulator pressure upon said valve to close same.

3. A hydraulic system comprising a co-nduit at system pressure, a conduit from an accumulator, a valve to open and close said conduits to one another, a preselector for operating said valve, means actuated by said preselector to open said valve under the influence of system pressure, and means actuated by said preselector to close said valve under the influence of accumulator pressure.

4. A hydraulic system comprising a conduit at system pressure, a conduit from an accumulator, a valve to open and close said conduits to one another, a preselector for operating said valve, means actuated by said preselector to cause valve operation under the influence of pressure in said system conduit, an element of said system having a pressure different from that of the system proper and the accumulator and subject to independent change, and means responsive to substantial element pressure to inhibit valve closing upon preselector adjustment to a closing position.

5. A hydraulic system comprising a conduit at system pressure, a conduit from an accumulator, a valve to open and close said conduits to one another, a preselector for operating said valve,

means actuated by said preselector to open said valve under the inuence of system pressure, means actuated by said preselector to condition said valve for closing under the influence of accumulator pressure, an element of said system having a pressure `different from that ofthe system proper and the .accumulator and subject to independent change, and means responsive to substantial element pressure to inhibit closing of said valve when said preselector is adjusted for valve closing, and to allow such closing when element pressure diminishes.

6. In a `hydraulic system having a conduit, a fluid pressure operated valve operable by pressure on opposite sides of the valve to open and close said conduit, an element of said system having a changeable hydraulic pressure substantially independent of the system proper but dependent as to its pressure on continued opening or closing of said valve, and means to direct the conduit fluid pressures for valve operation responsive to change in pressure in the system element.

7. In a hydraulic system having a conduit, a valve operable to ropen and close said conduit, a servo cell in said valve subject to conduit pressure and tending to open said Valve, a second servo cell in said valve subject at times to conduit pressure to overcome the pressure in the rst cell and to close said valve, and auxiliary valve means to open said second cell to conduit pressure, and to close said second cellv from said conduit pressure and simultaneously to vent said second cell, said auxiliary valve means comprising a manually operable selector movable to a valve operating position to close off said second cell from conduit pressure and movable to an alternate position, and a iiuid pressure responsive device cooperating with said selector and operable when said selector is in said alternate position to open said second cell to conduit pressure, said device being responsive in its operation to pressure unrelated to and independent of said conduit pressure and unrelated to manual operation of said selector.

8. In a hydraulic system having a conduit, a fluid pressure operated valve operable by conduit pressures on opposite sides of the valve to open and close said conduit, said hydraulic system having a changeable hydraulic pressure substantially independent of the conduit pressures but dependent upon operation of said system, and means to direct conduit uid for valve operation in response to decrease in said independent changeable hydraulic pressure.

9. In a hydraulic system having a conduit, a uid pressure voperated valve operable by conduit pressure on opposite sides of the valve to open and close said conduit, said hydraulic system having a changeable hydraulic pressure substantially independent of the conduit pressures but dependent upon operation of said system, means to direct conduit fluid for Valve operation in respons@ to decrease in said independent changeable hydraulic pressure, and manually operable means independent of said changeable pressure to direct conduit fluid for valve operation upon failure or non-existence of said independent pressure.

10. In a hydraulic system having a conduit, a valve housing and a main valve therein, conduits connected to said housing and one face of said main valve being exposed to the fluid pressure from one of said conduits at all times, a cylinder forming kpart of said housing, a piston in said cylinder, rigid With said main valve, said cylinder at times being connectible to the other of said conduits and said piston being movable to close said valve unit when .pressure from the other said conduit is admitted to said cylinder, a servo valve to open and close said cylinder to said other MAURICE E. CUSHMAN.

REFERENCES CITED The following references are of record in the le of this patent:

UNITED STATES PATENTS Number Name Date Johnson et al Apr. 18, 1882 Haskell Nov. 13, 1883 Wiedling Aug. 24, 1886 Schoefel Nov. 26, 1901 Nash Jan. 24, 1905 Schutte Aug. 17, 1909 Atkins Apr. 28, 1925 Abercrombie Dec. 8, 1931 Penick Nov. 22, 1932 Martin Apr. 16, 1946 

